US8484975B2 - Apparatus and method for start-up of a power plant - Google Patents

Apparatus and method for start-up of a power plant Download PDF

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Publication number
US8484975B2
US8484975B2 US12/026,203 US2620308A US8484975B2 US 8484975 B2 US8484975 B2 US 8484975B2 US 2620308 A US2620308 A US 2620308A US 8484975 B2 US8484975 B2 US 8484975B2
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United States
Prior art keywords
turbine
steam
combustion gas
heated combustion
steam turbine
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Expired - Fee Related, expires
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US12/026,203
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English (en)
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US20090193787A1 (en
Inventor
James West
Sam Draper
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General Electric Co
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General Electric Co
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Priority to US12/026,203 priority Critical patent/US8484975B2/en
Assigned to GENERAL ELECTRIC COMPANY reassignment GENERAL ELECTRIC COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DRAPER, SAM, WEST, JAMES
Priority to JP2009017849A priority patent/JP5476003B2/ja
Priority to CH00147/09A priority patent/CH698467B1/de
Priority to DE102009003425A priority patent/DE102009003425A1/de
Priority to CNA2009100040667A priority patent/CN101503976A/zh
Publication of US20090193787A1 publication Critical patent/US20090193787A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/101—Regulating means specially adapted therefor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • the present application relates to a start-up process for a combined cycle power plant.
  • Combined cycle power plants generally include a gas turbine, which utilizes the Brayton cycle, and a steam turbine, which utilizes the Rankine cycle. Greater efficiency may be achieved by utilizing a gas turbine and a steam turbine in combination than may be achieved by utilizing a gas turbine or a steam turbine independently.
  • a combined cycle power plant typically includes a gas turbine, a heat recovery steam generator, and a steam turbine.
  • a gas turbine is coupled with a generator to generate electricity.
  • An exhaust gas from the gas turbine is introduced into the heat recovery steam generator to generate a flow of steam.
  • the steam drives the steam turbine, which is coupled with a generator to generate additional electricity.
  • the overall start-up time for a combined cycle power plant is limited by the start-up time of the steam turbine.
  • Gas turbine start-up is fast relative to steam turbine start-up. During start up there is a relatively rapid increase in the exhaust temperature from the gas turbine. As the load of the gas turbine increases, a limit is reached on the exhaust temperature. A gas turbine controller then increases the airflow of the unit while maintaining the exhaust temperature limit.
  • the exhaust flow and exhaust temperature is directly related to the amount of energy discharged in the heat recovery steam generator and the steam temperature generated by the heat recovery steam generator.
  • Steam turbine start-up is slow relative to gas turbine start-up.
  • the start-up time of the steam turbine is limited by thermal stresses caused by temperature gradients between the rotor core and blades. These thermal stresses are monitored by measuring the temperature difference between the rotor and the steam at the inlet of the steam turbine.
  • the allowable steam inlet temperature is limited by the rotor temperature. As the rotor temperature increases, higher inlet steam temperatures are allowed. Because the steam turbine rotor temperature sets a limit on the allowable inlet steam temperature and the gas turbine exhaust temperature controls the steam temperature, the gas turbine may not increase in load until the steam turbine rotor is heated to a sufficient temperature. This may reduce revenue by causing the power plant to operate for an extended period at a lower efficiency condition.
  • Start-up emissions also may be increased because the load of the gas turbine may be too low for the combustor to operate in an efficient manner, thus causing concentrations of emissions such as NOx and CO to be greater than they would at higher load conditions.
  • a method and apparatus for warming a steam turbine during start-up of the gas turbine is desirable in order to reduce thermal stresses and decrease start-up times of a combined cycle power plant.
  • the present application provides a power plant.
  • the power plant may include a gas turbine having a compressor for producing compressed air and a combustor for combusting the compressed air with a combustible fuel to produce a heated combustion gas.
  • the power plant also may include a heat recovery steam generator for generating a flow of steam from an exhaust of the gas turbine and a steam turbine for expanding the flow of steam from the heat recovery steam generator.
  • the steam turbine may have a rotor having a rotor bore disposed axially therein.
  • the power plant also may include a conduit for directing at least a portion of the compressed air or at least a portion of the heated combustion gas from the gas turbine to the rotor bore of the steam turbine, wherein the compressed air or the heated combustion gas may warm the rotor bore of the steam turbine.
  • Another embodiment of the present application provides for a method of heating a steam turbine during start-up of a power plant having (i) a gas turbine having a compressor, a combustor, and a turbine for expanding a heated combustion gas, (ii) a heat recovery steam generator, and (iii) a steam turbine having a rotor having a rotor bore disposed axially therein.
  • the method of heating the steam turbine during start-up includes compressing ambient air in the compressor to produce compressed air, removing at least a portion of the compressed air from the compressor, and providing the compressed air to the rotor bore of the steam turbine, wherein the compressed air heats the rotor.
  • a further embodiment of the present application provides for a method of heating a steam turbine during start-up of a power plant having (i) a gas turbine having a compressor, a combustor, and a turbine for expanding a heated combustion gas, (ii) a heat recovery steam generator, and (iii) a steam turbine having a rotor having a rotor bore disposed axially therein.
  • the method of heating the steam turbine during start-up includes compressing ambient air in the compressor to produce compressed air, combusting the compressed air with a combustible fuel to produce a heated combustion gas, removing at least a portion of the heated combustion gas from the combustor, and providing the heated combustion gas to the rotor bore of the steam turbine, wherein the heated combustion gas heats the rotor.
  • FIG. 1 is a schematic view of a power plant of an embodiment of the present application as described herein.
  • FIG. 2 is a schematic view of a power plant of an embodiment of the present application as described herein.
  • FIG. 1 shows a schematic view of a power plant 10 of a particular embodiment of the present application.
  • the power plant 10 may include a gas turbine 11 , a heat recovery steam generator (“HRSG”) 12 , and a steam turbine 13 .
  • HRSG heat recovery steam generator
  • the gas turbine 11 may include a compressor 14 , a combustor 15 , and a turbine 16 .
  • ambient air 17 may be compressed by the compressor 14 to produce compressed air 18 .
  • the compressed air 18 may be provided to the combustor 15 along with a combustible fuel 19 .
  • the combustible fuel 19 may be combusted with the compressed air 18 to produce a heated combustion gas 20 .
  • the combustible fuel may include natural gas, hydrogen, propane, butane, isopropane, gasoline, diesel fuel, jet fuel, kerosene, ethanol, isopropyl alcohol, or synthetic gases derived from coal.
  • the heated combustion gas 20 then may be provided to the turbine 16 , wherein the heated combustion gas 20 may be expanded, thereby generating rotary work.
  • the turbine 16 may be coupled with a first generator 21 to generate electricity.
  • the exhaust 22 from the turbine 16 of the gas turbine 11 may be directed to the heat recovery steam generator 12 .
  • heat may be transferred from the gas turbine exhaust 22 to a feedwater flow 23 thereby generating a flow of steam 24 .
  • the cooled exhaust gas After flowing through the heat recovery steam generator 12 , the cooled exhaust gas then may be discharged to the atmosphere via a stack 25 .
  • the heat recovery steam generator 12 may include ductwork including finned tubes for the feedwater flow 23 . The hot exhaust gas may flow over the finned tubes, transferring a considerable portion of its heat to the feedwater flow, and thereby produce steam.
  • the flow of steam 24 from the heat recovery steam generator 12 then may be directed to the steam turbine 13 .
  • the steam turbine 13 may include a rotor 26 having a rotor bore 27 disposed axially therein.
  • the steam 24 may be introduced to the steam flow path 30 of the steam turbine 13 where it may be expanded, thereby generating rotary work.
  • the rotor 26 of the steam turbine 13 may be coupled with a second generator 28 to generate electricity.
  • both the gas turbine and the steam turbine may be coupled to the same generator to generate electricity.
  • the steam After exiting the steam turbine 13 , the steam may be dumped to a condenser 29 .
  • the gas turbine 11 may be brought to steady-state operation as quickly as possible.
  • Exhaust 22 from the gas turbine 11 may be directed to the heat recovery steam generator 12 which yields a flow of steam 24 .
  • a period of time may elapse before the heat recovery steam generator 12 is capable of generating steam at sufficient temperature and pressure to be introduced to the steam turbine 13 .
  • Introducing low temperature, low pressure steam to the steam turbine 13 could result in undesirable condensation within the steam turbine flow path 30 .
  • Steam may be dumped to the condenser 29 via conduit 31 until it reaches a sufficient temperature and pressure for introduction into the steam turbine 13 .
  • An outlet 32 may be provided for removing at least a portion of the compressed air 18 from the compressor 14 of the gas turbine 11 .
  • a compressor separate from the compressor 14 of the gas turbine 11 may be provided to supply compressed air.
  • the compressor separate from the compressor 14 of the gas turbine 11 may be powered by an electric motor, a piston engine, a gas turbine, a steam turbine, or another power source.
  • the portion of compressed air 18 may be provided to the rotor bore 27 of the steam turbine 13 via a conduit 33 .
  • the conduit 33 may include any means by which the compressed air 18 may be transmitted from the compressor 14 to the rotor bore 27 .
  • a valve 34 may be provided for controlling flow through the conduit 33 .
  • valve 34 may be opened to allow flow from the compressor 14 to the rotor bore 27 , thereby heating the rotor 26 before steam is introduced to the steam flow path 30 .
  • the valve 34 may be closed, thereby directing the compressed air through the turbine 16 to produce useful work.
  • the steam turbine 13 may include a system 35 for introducing the compressed air flow to the rotor bore 27 of the steam turbine 13 .
  • a second system 36 may be provided for removing the compressed air from the rotor bore 27 .
  • Systems suitable for introducing a flow to the rotor bore of a turbine are known to those of skill in the art. For example, a suitable system for introducing a gas to the rotor bore of a steam turbine is described in U.S. Pat. No. 5,498,131 to Minto. Once it exits the rotor bore 27 , the compressed air may be vented to the atmosphere.
  • FIG. 2 shows a schematic view of a power plant in accordance with an embodiment of the present application.
  • the power plant of FIG. 2 includes an outlet 37 for removing at least a portion of the heated combustion gas 20 from the combustor 15 of the gas turbine 11 .
  • the portion of heated combustion gas 20 may be provided to the rotor bore 27 of the steam turbine 13 via a conduit 33 .
  • a valve 34 may be provided for controlling flow through the conduit 33 .
  • a cooling system may be provided for cooling the conduit.
  • the valve 34 may be opened to allow flow from the combustor 15 to the rotor bore 27 , thereby heating the rotor 26 before steam is introduced to the steam flow path 30 .
  • the valve 34 may be closed, thereby directing the heated combustion gas 20 through the turbine 16 to produce useful work.
  • the steam turbine 13 may include a system 35 for introducing the heated combustion gas to the rotor bore 27 of the steam turbine 13 . Once the heated combustion gas passes through the rotor bore 27 of the steam turbine 13 , a second system 36 may be provided for removing the heated combustion gas from the rotor bore 27 . Once it exits the rotor bore 27 , the heated combustion gas may be vented to the atmosphere. In another embodiment, the heated combustion gas may be provided to the heat recovery steam generator 12 after passing through the rotor bore 27 .
  • the apparatus and methods of the present application may reduce thermal stresses and may decrease overall start-up times of combined cycle power plants.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Turbines (AREA)
US12/026,203 2008-02-05 2008-02-05 Apparatus and method for start-up of a power plant Expired - Fee Related US8484975B2 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US12/026,203 US8484975B2 (en) 2008-02-05 2008-02-05 Apparatus and method for start-up of a power plant
JP2009017849A JP5476003B2 (ja) 2008-02-05 2009-01-29 発電プラントの起動のための装置及び方法
CH00147/09A CH698467B1 (de) 2008-02-05 2009-02-02 Vorrichtung und Verfahren zum Anfahren eines Kraftwerkes.
DE102009003425A DE102009003425A1 (de) 2008-02-05 2009-02-03 Vorrichtung und Verfahren zum Starten eines Kraftwerkes
CNA2009100040667A CN101503976A (zh) 2008-02-05 2009-02-05 用于动力设备启动的装置和方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US12/026,203 US8484975B2 (en) 2008-02-05 2008-02-05 Apparatus and method for start-up of a power plant

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US20090193787A1 US20090193787A1 (en) 2009-08-06
US8484975B2 true US8484975B2 (en) 2013-07-16

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US (1) US8484975B2 (de)
JP (1) JP5476003B2 (de)
CN (1) CN101503976A (de)
CH (1) CH698467B1 (de)
DE (1) DE102009003425A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150226133A1 (en) * 2012-12-31 2015-08-13 Exxonmobil Upstream Research Company Gas turbine load control system
US20150345405A1 (en) * 2013-02-19 2015-12-03 United Technologies Corporation Gas turbine engine with rotor bore heating
US20160025014A1 (en) * 2014-07-25 2016-01-28 United Technologies Corporation High temperature disk conditioning system
US10174639B2 (en) 2017-01-31 2019-01-08 General Electric Company Steam turbine preheating system
US10337357B2 (en) 2017-01-31 2019-07-02 General Electric Company Steam turbine preheating system with a steam generator

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* Cited by examiner, † Cited by third party
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US8196395B2 (en) * 2009-06-29 2012-06-12 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8166766B2 (en) 2010-09-23 2012-05-01 General Electric Company System and method to generate electricity
US20120201661A1 (en) * 2011-02-07 2012-08-09 General Electric Company Contaminant shield system for a shaft
US8671688B2 (en) * 2011-04-13 2014-03-18 General Electric Company Combined cycle power plant with thermal load reduction system
US8893507B2 (en) * 2011-11-04 2014-11-25 General Electric Company Method for controlling gas turbine rotor temperature during periods of extended downtime
EP2642089B1 (de) * 2012-03-19 2016-08-24 General Electric Technology GmbH Verfahren zum Betrieb eines Kraftwerks
EP2738360B1 (de) 2012-12-03 2019-06-12 General Electric Technology GmbH Heizanordnung für eine Dampfturbine in einem Kraftwerk
EP2942493A1 (de) * 2014-05-06 2015-11-11 Siemens Aktiengesellschaft Wasserdampfkreislauf sowie ein Verfahren zum Betreiben eines Wasserdampfkreislaufes
US9890710B2 (en) * 2015-12-15 2018-02-13 General Electric Company Power plant with steam generation via combustor gas extraction
CN109296418B (zh) * 2017-07-25 2021-05-28 阿特拉斯·科普柯能源有限公司 用于从压力能到电能的能量转换的方法和设备

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JPS5649207U (de) 1979-09-25 1981-05-01
JPS5896102A (ja) 1981-12-02 1983-06-08 Hitachi Ltd 蒸気タ−ビンロ−タの暖機方法及びその装置
US5388960A (en) * 1992-10-05 1995-02-14 Kabushiki Kaisha Toshiba Forced-air cooling apparatus of steam turbine
US5473898A (en) 1995-02-01 1995-12-12 Westinghouse Electric Corporation Method and apparatus for warming a steam turbine in a combined cycle power plant
US5498131A (en) 1995-03-02 1996-03-12 General Electric Company Steam turbine with thermal stress reduction system
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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150226133A1 (en) * 2012-12-31 2015-08-13 Exxonmobil Upstream Research Company Gas turbine load control system
US10208677B2 (en) * 2012-12-31 2019-02-19 General Electric Company Gas turbine load control system
US20150345405A1 (en) * 2013-02-19 2015-12-03 United Technologies Corporation Gas turbine engine with rotor bore heating
US10094296B2 (en) * 2013-02-19 2018-10-09 United Technologies Corporation Gas turbine engine with rotor bore heating
US20160025014A1 (en) * 2014-07-25 2016-01-28 United Technologies Corporation High temperature disk conditioning system
US9995222B2 (en) * 2014-07-25 2018-06-12 United Technologies Corporation High temperature disk conditioning system
US10823085B2 (en) 2014-07-25 2020-11-03 Raytheon Technologies Corporation High temperature disk conditioning system
US10174639B2 (en) 2017-01-31 2019-01-08 General Electric Company Steam turbine preheating system
US10337357B2 (en) 2017-01-31 2019-07-02 General Electric Company Steam turbine preheating system with a steam generator

Also Published As

Publication number Publication date
JP5476003B2 (ja) 2014-04-23
JP2009185813A (ja) 2009-08-20
DE102009003425A1 (de) 2009-08-06
CH698467B1 (de) 2013-12-13
CN101503976A (zh) 2009-08-12
US20090193787A1 (en) 2009-08-06
CH698467A2 (de) 2009-08-14

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